US7341434B2 - Regulatory device comprising a threshold valve control valve - Google Patents

Regulatory device comprising a threshold valve control valve Download PDF

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Publication number
US7341434B2
US7341434B2 US10/505,208 US50520804A US7341434B2 US 7341434 B2 US7341434 B2 US 7341434B2 US 50520804 A US50520804 A US 50520804A US 7341434 B2 US7341434 B2 US 7341434B2
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Prior art keywords
pressure
control valve
control
delivery
threshold value
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US10/505,208
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US20050118036A1 (en
Inventor
Roland Belser
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Brueninghaus Hydromatik GmbH
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Brueninghaus Hydromatik GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure control

Definitions

  • the invention relates to a regulatory device to control a delivery volume for a pump with adjustable delivery volume.
  • a regulatory device for adjusting the delivery volume of a pump in the form of a hydrostatic piston machine is known from DE 43 29 164 A1, in which the delivery volume of the hydrostatic piston machine is regulated by both the delivery side working line pressure and the consumer input pressure supplied to the consumer after a choke point is supplied to the regulatory unit as input parameters.
  • the regulatory unit comprises two control valves arranged in a valve block which are each pressurised on a first measurement surface with the delivery-side working line pressure. In the opposite direction a spring acts on a first control valve and the consumer input pressure taken from the consumer supply line acts on the second control valve.
  • the control valves are set so that the first control valve pressurises a control pressure chamber of an actuator from the working line when a limit value which can be set by the spring is exceeded. By pressurising the control pressure chamber the hydrostatic piston machine is adjusted in the direction of lower delivery.
  • the regulation is performed by the second control valve where the control pressure chamber of the actuator is either pressurised from the working line or pressure-relieved against the tank volume.
  • the control pressure chamber of the actuator is either pressurised from the working line or pressure-relieved against the tank volume.
  • a constant pressure ratio is maintained between the delivery-side working pressure and the consumer input pressure.
  • the pressure difference between the working line and the consumer input is proportional to the delivery volume, with the circuit described the hydrostatic piston machine can be regulated to a constant delivery volume.
  • the regulatory device has the disadvantage that as the consumer input pressure diminishes, the second control valve pressurises the control pressure chamber of the actuator so that the pressure in the working line can fall to almost zero. If further consumer or control devices which require a minimum pressure are connected to the working line, these devices can no longer be operated.
  • the object of the invention is to create a regulatory device to set a constant delivery volume of a pump which maintains the minimum pressure in a working line irrespective of the consumer input pressure.
  • the regulatory device has the advantage that different input pressures are used to control a first and a second control valve which together constitute the regulatory unit.
  • a first control range in which a minimum pressure can be set by the threshold value control valve
  • a second control range in which above a limit value defined by the threshold value control valve a constant delivery quantity of the pump can be set by the delivery flow control valve.
  • the constant delivery quantity is regulated by the delivery flow control valve as a function of the consumer input pressure and a pressure present at a measurement surface, where the pressure present is the output pressure from the threshold value control valve. This prevents, on diminishing consumer input pressure, the control pressure chamber of an actuator being pressurised by the delivery flow control valve until the delivery volume of the hydrostatic piston machine is set at zero.
  • the sub-claims define advantageous refinements of the regulatory device according to the invention.
  • FIG. 1 a hydraulic circuit diagram of a regulatory device according to the invention.
  • FIG. 2 a section through a control valve unit according to the invention arranged in a control valve block.
  • FIG. 1 shows a hydraulic circuit diagram of the regulatory device 1 according to the invention.
  • the regulatory device 1 acts on the swivel angle of an adjustable pump in the form of a hydrostatic piston machine 2 .
  • a control valve unit 3 is provided by means of which the control pressure predominating in a return element 5 can be regulated.
  • the return element 5 sets the swivel angle of the hydrostatic piston machine 2 which is driven via a drive shaft 6 .
  • the hydrostatic piston machine 2 delivers a pressure medium into a working line 7 . Via the working line 7 the pressure medium reaches a consumer supply line 8 to which is connected a consumer not shown. Between the working line 7 and the consumer supply line 8 are arranged in series a choke 9 and an adjustable choke 10 .
  • the choke 9 need not be designed in detail but can be produced by the choking effect of the line length.
  • Also connected with the consumer supply line 8 is a pressure limiting device 11 .
  • the consumer supply line 8 can be depressurised to a tank volume 13 via the pressure limiting device 11 , depressurisation occurring when the pressure in the consumer supply line 8 rises above a threshold value which can be prespecified by means of an adjustment spring 12 .
  • the swivel angle of the hydrostatic piston machine 2 is adjusted by means of an actuator 4 and the return element 5 .
  • the actuator 4 can be omitted and an adjustment in the direction of greater deflection can be generated by a spring acting on the return element 5 .
  • the actuator 4 is connected with the working line 7 via a connecting line 14 .
  • the pressure predominating in the working line 7 is thus supplied to a pressure chamber 15 of the first actuator 4 , where it co-operates with the force of a pretension spring 16 on a control piston 17 .
  • the force applied to the control piston 17 in the control pressure chamber 15 of the first actuator 4 is directed so that it adjusts the hydrostatic piston machine 2 in the direction of greater swivel angles.
  • the control valve unit 3 sets a control pressure which acts in the second actuator 5 .
  • the control valve unit 3 is connected by means of a further connecting line 18 with the working line 7 on one side and with the consumer supply line 8 via a consumer input pressure supply line 19 .
  • the control valve unit 3 is supplied with the pressure predominating before and after the choke points 9 and 10 respectively.
  • the control valve unit 3 thus regulates on the basis of the falling pressure at the choke points 9 and 10 .
  • the control valve unit 3 is connected via a control pressure line 20 with a control pressure chamber 21 which is arranged in the actuator 5 .
  • the control pressure predominating in the control pressure chamber 21 acts on a control piston 42 and adjusts the hydrostatic piston machine 2 in the direction of smaller swivel angles.
  • a spring can be arranged in the second actuator 5 which subjects the control piston 42 to a force acting against the pressure of the control pressure chamber 21 .
  • the control valve unit 3 comprises a threshold value control valve 22 and a delivery flow control valve 23 .
  • the threshold value control valve 22 is pretensioned with a first spring 24 so that in the pressureless state it is in the starting position shown in FIG. 1 .
  • the delivery flow control valve 23 is also pretensioned by a second spring 25 and is also in its starting position in the pressureless state.
  • the threshold value control valve 22 has a delivery pressure measurement connection 26 where the pressure present at the delivery pressure measurement connection 26 opposes the force of the first spring 24 . As the pressure rises, the threshold value control valve 22 is deflected from its starting position towards its second end position.
  • the control pressure measurement connection 27 of the delivery flow control valve 23 is connected via a control pressure channel 30 with the threshold value control valve 22 .
  • a first control pressure connection 31 of the delivery flow control valve 23 is connected with a relief line 32 which is connected to a pressure relief connection 33 of the delivery flow control valve 22 .
  • the relief line 32 is connected with the tank volume 13 .
  • the threshold value control valve 22 has a second control pressure connection 34 and a third control pressure connection 35 via which the control pressure chamber 21 is connected via the control pressure line 20 with the first control pressure connection 31 of the delivery flow control valve 23 .
  • the return pressure chamber 21 is connected with the tank volume 13 .
  • the pressure taken via the further connecting line 18 from the working line 7 is supplied firstly to the delivery pressure measurement connection 26 and secondly, via a line branching from the supply line, to a delivery pressure input 36 of the threshold value control valve 22 .
  • the delivery pressure input 36 is connected in the second end position of the threshold value control valve 22 with a delivery pressure outlet 37 .
  • the delivery pressure outlet 37 is connected via the control pressure channel 30 with both the control pressure measurement connection 27 and with a control pressure supply connection 38 .
  • control pressure supply connection 38 is connected with the first control pressure connection 31 so that the return pressure chamber 21 is pressurised from the working line 7 via the threshold value control valve 22 and the delivery flow control valve 23 .
  • a further adjustable choke 39 is arranged between the control pressure line 20 and the relief line 32 .
  • the hydrostatic piston machine 2 In the pressureless state, first via the pretension spring 16 of the actuator 4 the hydrostatic piston machine 2 is swivelled to a great delivery volume. If the hydrostatic piston machine 2 is driven via the drive shaft 6 , this generates a pressure in the working line 7 which is supplied via the connection line 14 in the control pressure chamber 15 of the first actuator 4 .
  • the first actuator 4 as the pressure in the working line 7 increases, therefore attempts to adjust the hydrostatic piston machine 2 further in the direction of greater swivel angles.
  • the rising pressure in the working line 7 is supplied via the further connecting line 18 to the threshold value control valve 22 and subjects the delivery pressure measurement connection 26 to a hydraulic force.
  • the control pressure chamber 21 of the second actuator 5 is connected with the tank volume 13 so that no force is generated by the second actuator 5 to counter the control force of the first actuator 4 .
  • the pressure in the working line 7 present at the delivery pressure measurement section 26 moves the threshold value control valve 22 in the direction of its second end position and thus, at a limit value preset by the adjustable spring 24 , connects the delivery pressure input 36 with the delivery pressure output 37 .
  • This regulatory pressure supplied to the delivery flow control valve 23 above the limit value also regulates the delivery flow control valve 23 in this range.
  • the delivery flow control valve 23 as the control pressure rises, is moved further in the direction of its second end position by the pressurisation of the control pressure measurement connection 27 so that via the control pressure supply connection 38 , and subsequently via the first, second and third control pressure connections 31 , 34 and 35 , the control pressure chamber 21 is subjected to a control pressure.
  • the control pressure chamber 21 is pressurised with a control pressure as described above a limit value adjustable via the threshold value control valve 22 for the pressure in the working line 7 , so that a return force countering the control force of the actuator 4 is only generated above a particular minimum pressure in the working line 7 .
  • This measure maintains a minimum pressure in the working line 7 even if the pressure in the consumer supply line 8 falls to zero.
  • the control pressure in the control pressure chamber 21 is set via the delivery flow control valve 23 so that at the delivery flow valve 23 a force equilibrium is set.
  • the force equilibrium is composed of the force of the second spring 25 and the two hydraulic forces which act on the control pressure measurement connection 27 and the comparison pressure connection 29 .
  • Above the pressure preset by the threshold value control valve 22 thus a return control force is regulated with which a constant pressure difference is set between the working line 7 and the consumer supply line 8 .
  • a constant pressure difference is here equivalent to a constant delivery volume.
  • shut-off valve 40 which in normal operation connects the consumer supply line 8 with the comparison pressure connection 29 .
  • the shut-off valve 40 can be activated via a control lever 41 so that the comparison pressure connection 29 can be connected via the consumer input pressure supply line 19 with the tank volume 13 .
  • Activation of the control lever 41 leads to a pressure relief at the comparison pressure connection 29 .
  • the force applied to the control pressure measurement connection 27 at the delivery flow control valve 23 predominates so that the control pressure chamber 21 is pressurised and the hydrostatic piston machine 2 is adjusted in the direction of a smaller swivel angle.
  • the threshold value control valve 22 is consequently adjusted in the direction of its starting position so that a lower pressure is supplied to the control pressure channel. Due to the lower control pressure supplied via the control pressure channel 30 to the control pressure measurement connection 27 , the delivery flow control valve 23 is also adjusted in the direction of its starting position so that the control pressure chamber 21 is depressurised to the tank volume 13 when the working line pressure falls below the threshold pressure.
  • a minimum pressure which can be preset by the setting of the threshold value control valve 22 . This can be utilised to operate further control devices or further consumers which require a minimum pressure.
  • One application for example, is in mobile devices where the control of the mobile valve is supplied via pressure reducers from the working pressure and their function must be retained even on standby.
  • FIG. 2 A preferred constructional embodiment is shown in FIG. 2 .
  • the threshold value control valve 22 and the delivery flow control valve 23 are arranged in a control valve block 43 .
  • the control valve block 43 is made a first receiver bore 44 and a second receiver bore 45 , the centre axes of the receiver bores 44 and 45 being preferably aligned parallel.
  • a threshold value control valve piston 46 and in the second receiver bore 45 a delivery flow control valve piston 47 .
  • the threshold value control valve piston 46 and the delivery flow control valve piston 47 are smaller in their radial extension than the respective diameters of the first receiver bore 44 and the second receiver bore 45 respectively, and arranged axially displaceable in the receiver bores 44 and 45 .
  • the delivery flow control valve piston 47 at its ends has a first guide section 48 and a second guide section 49 , where the radial extension of the guide sections 48 and 49 corresponds to the radial extension of the second receiver bore 45 so that the delivery flow control valve piston 47 is guided in the receiver bore 45 .
  • a control section 50 at which are formed a first control edge 51 and a second control edge 52 .
  • a control pressure chamber 53 is formed between the first guide section 48 and the control section 50 , because of the different radial extensions of the delivery flow control valve piston 47 and the second receiver bore 45 . Furthermore, between the control section 50 and the second guide section 49 can be provided a further guide section 55 .
  • the threshold value control valve piston 46 is formed corresponding to the delivery flow control valve piston 47 and has a first guide section 56 and at its second end a second guide section 57 with which the threshold value control valve piston 46 is guided in the first receiver bore 44 . Between the first guide section 56 of the threshold value control valve piston 46 and a control section 58 of the threshold value control valve piston 46 is also formed a delivery pressure chamber 61 by the different radial extensions of the threshold value control valve piston 46 and the first receiver bore 44 .
  • the control section 58 of the threshold value control valve piston 46 also has a first control edge 59 and a second control edge 60 .
  • first pressure chamber 63 On the face of the first guide section 56 is formed a first pressure chamber 63 which is connected via an overflow channel 62 with the delivery pressure chamber 61 .
  • the pressure predominating in the delivery pressure chamber 61 subjects the threshold control valve piston 46 on a face 64 with a hydraulic force which acts in the axial direction on the threshold value control valve piston 46 .
  • the force of the first spring 24 which rests on a spring bearing 65 acts on the threshold value control valve piston 46 , the spring bearing 65 being actively connected with the threshold value control valve piston 46 .
  • a seat 66 is formed on the face of the second guide section 57 , where the spring bearing 65 has a recess corresponding to the seat 66 .
  • a counter bearing 67 which rests on a set screw 68 .
  • the distance between the spring bearing 65 and the counter bearing 67 can be varied so that the pretension of the first spring 24 can be set.
  • a lock nut 69 is provided to fix the set screw 68 .
  • the open end of the set screw 68 is covered with a cap nut 70 and hence protected from soiling.
  • the lock nut 69 and the cap nut 70 are each sealed via a sealing element, preferably an 0 -ring 71 , against a housing component or against each other.
  • the counter bearing 67 , the set screw 68 , the lock nut 69 and the cap nut 70 together form an adjustment device 72 .
  • a spring chamber 73 is provided in the control valve block 43 .
  • a connecting bore 74 is made in the control valve block 43 .
  • the connecting bore 74 opens into a tank connecting bore 75 , where a tank connecting piece 76 is on the outside of the control valve block 43 .
  • a return line is connected to the tank connecting piece 76 , for example, which is connected with a tank volume 13 .
  • a delivery pressure connection 78 is provided on the outside of the control valve block 43 .
  • the pressure supplied via the further connection line 18 from the working line 7 is passed to the control valve block 73 .
  • the delivery pressure connection 78 is connected with a delivery pressure channel 79 which opens into the delivery pressure chamber 61 .
  • the threshold value control valve piston 46 Due to the pressure predominating in the first pressure chamber 63 , the threshold value control valve piston 46 is subjected to an axial force which moves the threshold value control valve piston 46 in FIG. 2 to the right against the force of the first spring 24 . This moves the first control edge 59 on the control section 58 of the threshold value control valve piston 46 also to the right where, on passing of a threshold value which can be set via the adjustment device 72 , it releases a flow channel from the delivery pressure chamber 61 to the control pressure channel 30 . In addition to the force of the first spring 24 , the pressure predominating in the spring chamber 73 of the tank volume 13 acts on the threshold value control valve piston 46 .
  • the pressure medium supplied via the control pressure channel 30 to the control pressure chamber 53 is passed via a further overflow channel 80 to the second pressure chamber 81 which is formed on the face of the delivery flow control valve piston 47 and in which the pressure exerts a force on the face 82 of the delivery flow control valve piston 47 .
  • the second receiver bore 45 is also fitted with a closing piece 83 and a sealing element 84 , where the closing piece 83 is also secured with a screw connection in the control valve block 43 .
  • the delivery flow control valve piston 47 is deflected from its starting position shown in FIG. 2 towards the right until a force equilibrium has been set between the control pressure acting on the face 82 and the opposing forces.
  • a further spring bearing 94 which is actively connected with the tapered seat 93 of the delivery flow control valve piston 47 .
  • a second spring 25 rests on the further spring bearing 94 , where the second spring 25 can also be supplemented by an additional spring 25 ′ which also rests on the further spring bearing 94 .
  • the second spring 25 and the additional spring 25 ′ rest on a counter bearing of a further adjustment device 95 which is constructed corresponding to the adjustment device 72 and which will not be described further.
  • the second spring 25 and the additional spring 25 ′ are arranged in a spring chamber 96 .
  • the spring chamber 96 is connected via a consumer input pressure supply line connection 97 and a consumer pressure channel 98 via the consumer pressure supply line 19 described in FIG. 1 with the consumer pressure channel 98 .
  • in spring chamber 96 act both the forces of the two springs 25 and 25 ′ and a hydraulic force proportional to the consumer input pressure as long as the shut-off valve 40 is not operated.
  • the delivery flow control valve piston 47 is moved to the right from its starting position shown in FIG. 2 .
  • the first control edge 51 releases a flow channel from the control pressure chamber 53 into a control pressure channel 85 .
  • the control pressure channel 85 is formed as a bore in the control valve block 43 .
  • the second control edge 52 of the delivery flow control valve piston 47 interrupts a flow path between the control pressure channel 85 and the tank connection bore 75 .
  • the tank connection bore 75 and the control pressure channel 85 are connected together in the starting position of the delivery flow control valve 23 by the different diameters of the delivery flow control valve piston 47 and the second receiver bore 45 .
  • the control pressure channel 30 , the control pressure channel 85 and the tank connecting bore 75 are made as bores in the control valve block 43 .
  • the three bores lie in one plane and are connected together via the connecting bore 74 , where the connecting bore 74 is divided into several sections.
  • Between the tank connecting bore 75 and the control pressure channel 85 is formed a second section of the connecting bore 74 , and between the control pressure channel 85 and the control pressure channel 30 a third section of the connecting bore 74 .
  • a first stopper 86 which has a blind bore 87 from the control pressure channel 85 .
  • the stopper 86 has a choke opening 88 and a connecting opening 89 .
  • a flowable connection is created between the third section 74 b of the connecting channel 74 and the set pressure channel 85 via the blind bore 87 .
  • the choke opening 88 however by twisting the stopper 86 is brought into partial overlap with the second section 74 a, the first section, of the connecting bore 74 so that here an adjustable choke is formed between the set pressure channel 85 and the connecting bore 74 .
  • the control pressure channel 30 also formed as a bore in the control valve block 43 is closed with a further stopper 90 in which a further blind bore 92 is made from the outside, where the further blind bore 92 is connected via a further connecting opening 90 with the third section 74 b of the connecting bore 74 .
  • Pressurisation of the actuator 5 described in FIG. 1 takes place starting from the movement described above of the threshold value control valve piston 46 and the delivery flow control valve piston 47 from the set pressure channel 85 via the blind bore 87 and the connecting opening 89 and the third section 74 b of the connecting bore 74 , then via the connecting opening 91 and the further blind bore 92 from where a line section not shown which corresponds to the control pressure line 20 in FIG. 1 leads to the set pressure chamber 21 of the actuator 5 .
  • shut-off valve 40 leads to a reduction of the pressure in the further spring chamber 96 .
  • the resulting setting movement of the delivery flow control valve piston 47 to the right is prevented by the falling pressure in the working line 7 , as the first control edge 59 on the control section 58 of the threshold value control valve piston 46 closes the flow path between the delivery pressure chamber 61 and the control pressure channel 30 .
  • the pressure in the second pressure chamber 81 is relieved via the choke opening 88 into the tank volume 13 so that the delivery flow control valve piston 47 is moved in the direction of its starting position because of the forces of the two springs 25 and 25 ′.
  • the return movement of the delivery flow control valve piston 47 causes the second control edge 52 of the control section 50 to release the flow path from the control pressure channel 85 to the tank connecting bore 75 .
  • the control pressure chamber 21 is thus depressurised into the tank volume 13 so that as described in FIG. 1 , the control force opposing the actuator 4 is relieved and hence the swivel angle of the hydrostatic piston machine 2 set so that a particular minimum pressure predominates in the working line 7 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
US10/505,208 2002-05-03 2003-04-04 Regulatory device comprising a threshold valve control valve Expired - Fee Related US7341434B2 (en)

Applications Claiming Priority (3)

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DE10219850A DE10219850B3 (de) 2002-05-03 2002-05-03 Regeleinrichtung mit Grenzwertregelventil
DE102198500 2002-05-03
PCT/EP2003/003542 WO2003093676A1 (de) 2002-05-03 2003-04-04 Regeleinrichtung mit grenzwertregelventil

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US7341434B2 true US7341434B2 (en) 2008-03-11

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US (1) US7341434B2 (de)
EP (1) EP1502027B1 (de)
DE (2) DE10219850B3 (de)
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CN103097742A (zh) * 2010-04-16 2013-05-08 罗伯特·博世有限公司 压力流量调节器
US20140103233A1 (en) * 2012-10-17 2014-04-17 Robert Bosch Gmbh Hydraulic valve arrangement and hydraulic machine arrangement having a valve arrangement of this kind
US20140174549A1 (en) * 2012-12-21 2014-06-26 Eaton Corporation Proportional flow control of a fluid pump assembly

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US6874318B1 (en) * 2003-09-18 2005-04-05 Sauer-Danfoss, Inc. Automatic remote pressure compensation in an open circuit pump
FI123639B (fi) * 2005-04-15 2013-08-30 Sandvik Mining & Constr Oy Menetelmä ja sovitelma kallionporauksen ohjaamiseksi
DE102005035981A1 (de) * 2005-07-28 2007-02-01 Putzmeister Ag Hydraulische Schaltungsanordnung, insbesondere für den Antrieb von Betonverteilermasten
CN104912764B (zh) * 2015-05-20 2017-03-15 北京航空航天大学 直驱型电控比例无级调压变量柱塞泵
CN105736491B (zh) * 2015-05-20 2017-09-22 北京航空航天大学 基于自减压恒压阀的恒压变量柱塞泵
DE102016119310B4 (de) * 2016-10-11 2024-08-08 Danfoss Power Solution a.s. Verbessertes Fluidsteuerventil

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DE4329164A1 (de) 1993-08-30 1995-03-09 Brueninghaus Hydraulik Gmbh Verwendung eines hydraulischen Steuerventilblocks mit einem Sitzventil anstelle eines Kolbenventils
DE10006659A1 (de) 2000-02-15 2001-08-23 Brueninghaus Hydromatik Gmbh Regeleinrichtung für eine Hydropumpe
US6311489B1 (en) 1997-09-24 2001-11-06 Brueninghaus Hydromatik Gmbh Regulating device for an adjustable hydraulic pump with several consumers

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US4810171A (en) * 1986-12-30 1989-03-07 Brueninghaus Hydraulik Gmbh Regulator for an adjustable hydrostatic machine
DE4329164A1 (de) 1993-08-30 1995-03-09 Brueninghaus Hydraulik Gmbh Verwendung eines hydraulischen Steuerventilblocks mit einem Sitzventil anstelle eines Kolbenventils
US6311489B1 (en) 1997-09-24 2001-11-06 Brueninghaus Hydromatik Gmbh Regulating device for an adjustable hydraulic pump with several consumers
DE10006659A1 (de) 2000-02-15 2001-08-23 Brueninghaus Hydromatik Gmbh Regeleinrichtung für eine Hydropumpe

Cited By (7)

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Publication number Priority date Publication date Assignee Title
CN103097742A (zh) * 2010-04-16 2013-05-08 罗伯特·博世有限公司 压力流量调节器
US20130199631A1 (en) * 2010-04-16 2013-08-08 Christian Spielvogel Pressure/Flow Regulator
US9441747B2 (en) * 2010-04-16 2016-09-13 Robert Bosch Gmbh Pressure/flow regulator
US20140103233A1 (en) * 2012-10-17 2014-04-17 Robert Bosch Gmbh Hydraulic valve arrangement and hydraulic machine arrangement having a valve arrangement of this kind
US9399985B2 (en) * 2012-10-17 2016-07-26 Robert Bosch Gmbh Hydraulic valve arrangement and hydraulic machine arrangement having a valve arrangement of this kind
US20140174549A1 (en) * 2012-12-21 2014-06-26 Eaton Corporation Proportional flow control of a fluid pump assembly
US9323253B2 (en) * 2012-12-21 2016-04-26 Eaton Corporation Proportional flow control of a fluid pump assembly

Also Published As

Publication number Publication date
DE10219850B3 (de) 2004-02-05
EP1502027A1 (de) 2005-02-02
EP1502027B1 (de) 2006-05-31
US20050118036A1 (en) 2005-06-02
WO2003093676A1 (de) 2003-11-13
DE50303587D1 (de) 2006-07-06

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